Machine tool transmission and control mechanism



7 Sheets-Sheet 1 INV NT OR ATTORNEY -g- 1941- w. I. SENG E R.

MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed Jan. 27, 1939 y v @hfi! um i TlL IIIIII F Aug. 5, 1941.

w. 1. SENGER MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed Jan. 27, 1939 7 Sheets-Sheet 2 RQM INVENTQR BY 4 7 Q ATTORNEY Aug. 5, 1941.

W. l. SENGER MAGHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed Jan. 27, 19-39 ATT RgY L 7 Sheets-Sheet 3 Aug. 5, 1941. w. SENGER MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM 7 Sheets-Sheet 4 Filed Jan. 27, 1939 w RN 7 w B s wiw s Qkfik 9w 3% R iili:\

iv Q fi Q iv wwwhdh 3 0% iv N INVENTOR 1 ATTQNEY A g 5, 1941? w. SENGER 2,251,619 MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM 7 Filed Jan. 27, 193 9 7 Sheets-Sheet 5 Y m. Wm T R m m M A Maw QQQ M 8 w QQ 3 QQ Q R MN QN 0R v m g- 1941- w. l. SE NGER 2,251,619

MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Filed Jan. 27, 19:59

7 Sheets-Sheet 6 m IIIIIIIII INVENTOR N N BY I ATTORNEY Aug. 5, 1941; w. sENGER 2,251,619 MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM 7 Sheets-Sheet 7 ATTQRNEY IIIIIIIl'IIII Filed Jan. 27. 1959 Patented Aug. 5, 1941 MACHINE TOOL TRANSMISSION AND CONTROL MECHANISM Werner Irving Senger, Madison, Wis., assignor to Gisholt Machine Company, Madison, Wis., .a corporation of Wisconsin Application January 27, 1939, Serial No. 253,095

15 Claims.

This invention relates tomachine tools and more particularly to transmission and control mechanism for lathes.

A purpose of the invention is to efiect a machine tool including an improved transmission and 'control mechanism for relative bodily movement of a work piece and tool, and particularly for bodily movement of -a lathe tool longitudinally and transversely on the lathe bed.

Another purpose is to effect a machine tool including transmission mechanism in an improved form for, relative work and tool movement both ata cutting or feed rate, and at an idle or quick traverse rate, and improved control mechanism both for the manualand automatic control of such movements, and particularly for lathes.

Another purpose is to provide transmission and control mechanism particularly adapted for use with, and supplemental to, the transmissionand control mechanism shown in ace-pending application, Serial No. 120,343, filed January 13, 1937. Another purpose is to generally simplify and improve the construction and operation of transmission and control mechanism for one or more of the purposes previously mentioned, and particularly for lathes, and still other purposes will be apparent from this specification.

The invention comprises the construction, combination and relationship of parts as herein illustrated, described'and claimed, and such modifications of the structure illustrated anddescribed as are equivalent to the claims.

The same reference characters have been used to identify the same parts throughout, and in the drawings:

Figure l is a front elevation of a lathe incorporating the invention.

Figure 2 is an enlarged 'front elevation partly in section, of a tool carriage portion of the lathe of Fig. 1.

Figure 3 is an end elevation of the same tool carriage and its support viewed from the right in Fig. 2 and partly in section.

Figure 4 is a sectional development of some of the transmission mechanism of the tool carriage of Fig. 2, taken along line "4-4 of Fig. 3.

Figure 5 is a partial vertical section through the tool carriage of Fig. 2, taken along line 5--5 of Fig. 2.

Figure 6 is a partial plan view of the upper slide of the tool carriage of Fig. 2.

Figure 7 is a rear view of a front plate of the tool carriage of Fig. 2 and of certain mechanism carried thereon.

Figure 8 is a vertical section taken approximately along line 88 of Figs. 2 and 7.

Figure 8A is a fragmental section taken along line 8A8A-o'f Fig. 8.

Figure 9 is a partial top view of some of the mechanism shown in Figs. 2 and 7, viewed from line 9-9 of Fig. 8.

Figure 10 is a partial sectional development showing a hand wheel train in the carriage of Figs. 2 and '7, the development being substantially along line Ill-HI of Fig. 7.

Figure 11 is a partial vertical section taken approximatelyalong the line I l-I I of Figs. 2 and 7.

Figure 12 is a partial section taken approximately along line l'2-I2 of Figure 11.

Figure 13 is a partial section taken approximately along line l3l3 of Fig-11.

' Figure 14 is a partial section taken along line M- -l4 of Fig. 2.

Figure 15 is a fragmentary sectiontaken along line I5-|5 of Fig.2.

The lathe shown in Fig. 1 includes a bed 20, and a headstock portion generally denoted by the numeral 2| in which is rotatably-mounted a work spindle 22 for which there is provided suitable transmission and control mechanism for effecting various spindle speeds in either direction. The spindle transmission and control mechanism may, for example, be similar to that shown in the Patent No. 2,054,141, issued September 15, 1936, and includes rate change elements which may be shifted into a variety of speed position combinations upon operation of a selective speed controller, such as the controller 23, the spindle transmission also including clutch and brake means in part controlled by the controller 23 and in part by a hand lever such as 24.

The lathe also includes a carriage generally denoted by the numeral 26,Fig. 1, which includes a main portion 21, guided on suitable slides or ways on bed 20 for reciprocatory movement parallel with the axis of spindle 22, a cross slide 28 guided on the portion 21 for reciprocatory movement transverse to the movement of portion 21, and a tool holder 29 mounted on the cross-slide 28 and adapted to rigidly support suitable tools for operation on Work pieces carried by spindle 22. The bed 20 is extended to the right in Fig. 1 to similarly guide a second tool carriage generally indicated by the numeral 3!] which, as here shown, is substantially identical in construction and operative mechanism with the carriage 26.

Adjacent the front of the bed 20 there is a screw 3| which is fixed against both rotation and axial movement relative to the bed 20, and transmission shafts 32, 33 which respectively serve to transmit a feed rate drive to the different carriages 26, 3t]. Each of the feed rate shafts is driven from the spindle 22 as, for example, from a gear 34, Fig. I, but through different rate change mechanism, not here shown, separately controlled for rate selection from hand levers 35, 35 respectively mounted on the carriage which is driven from the corresponding feed rate shaft, the rate changers being carried by a unit generally denoted by the numeral 31, and respectively connected for control from the different hand levers by shafts 38 and 39. A quick traverse rate shaft 40 is also adjacent the front of bed 20, and

is driven at a relatively rapid rate from a motor, such as motor 40a, Fig. l. Shaft 40 serves to transmit quick traverse rate drive to either of the carriages 25, 30 according to control mechanism later described.

The trains connecting the spindle gear 34 with each of the feed rate shafts 32, 33, and the mechanism for controlling the rate changers of each of these trains, as well as the transmission mechanism connecting motor 45a with the quick traverse rate shaft 40 is, preferably, the same as the mechanism fully disclosed'in said co-pending application, Serial No. 120,343, and therefore will not here be described.

The transmissions connecting the feed rate shafts 32, 33 and quick traverse'rate shaft .40

for longitudinal'movement of the carriages 26, 39 and for transverse movement of the respective cross slides, as well as the control mechanism therefor, is substantially identical for each carriage, and will therefore be described in detail only for the carriage 26.

Referring to Figs. 3, 4,the stationary screw 3| extends through a suitable bore in'the carriage apron, there being a sleeve nut device. 4| engaged by the screw and rotatably supported but fixed against axial movement relative to the carriage by suitable bearings such as 42, 43. Nut device 4| includes a sleeve portion Ma and the nut portions 45b, 450 each engaging screw 3| and relatively axially adjustable for eliminating back lash.

A sleeve device 44, Fig. 4, rotatably supported by bearings 45, 45, is co-axial with feed shaft 32 and comprises bushing portions 44a, 44b having internal hexagon bores engaging the hexagon exterior of the feed shaft to drive the sleeve device. A similar sleeve device 41, having bushings 41a, 41b, is co-axial with the feed shaft 33 but in the carriage 25 is not utilized except to rotatably support reverser gearing, later described. Another sleeve device 48, similarly to the device 44, is provided with bushings 48a, 48b which provide hexagon bores to drive the sleeve 48 from the quick traverse shaft 45.

The several sleeve devices 4|, 44, 41, 48, Fig. 4, are interconnected to provide quick traverse reverser and feed reverser devices respectively operative between the quick traverse shaft 40 and feed shaft 32 and the nut sleeve device 4| whereby to provide alternative longitudinal feed or quick traverse rate to the carriage 26, in either direction, as follows:

For quick traverse rate drive of the nut device 4| there is provided a reverser clutch generally denoted by the numeral 49, Fig. 3, which includes a plurality of spaced outer clutch members 49a, 4% respectively associated with groups of clutch friction plates 49c, 49d, the plates of each group being slidably alternately keyed with the associated outer clutch member and with the sleeve 48, the plates of the different groups being alternatively engageable, to selectively drive the different outer clutch members 49a, 49?), by the means of an axially slidable clutch spool 430 which may be shifted in either axial direction to set up the drive through the one or the other clutch member 49a, 49?), or to position the spool centrally to interrupt the drive, by the means of suitable shifter means, later more fully described, including a fork member 58, Figs. 4, 7, engaging an annular groove in the spool.

The quick traverse reverser clutch members 45a, 4% are each connected with carriage nut sleeve 4|, respectively through the train of gears comprising gears 5|, 52, 53, and through the train comprising gears 54, 55, 56, 5?, 55, the arrangement being such that shifting of the clutch spool 55 in the one direction drives the carriage sleeve nut 4| at quick traverse rate in the one direction and opposite shifting of the spool drives the sleeve nut in the other direction, while an in 'termediate position of the spool disengages both groups of friction plates 49c, 45d and permits the sleeve nut to be driven at feed rate, or to remain stationary. It will be understood that the gears 5|, 52, also 54, 55, also 57, 58, although not shown meshed in the developed section, Fig. 4, are meshed in driving engagement in the actual shaft position shown in Fig. 3.

For feed rate drive of the nut sleeve 4| there is provided a feed reverser clutch generally denoted by the numeral 59, Fig. 4. Clutch sleeves 59a, 5% are rotatably supported on the sleeve 44 and respectively provided on their inner adjacent ends with clutch jaws 59c, 59d. A clutch member 59c is slidably keyed on sleeve 44 and positioned between the sleeves 53a, 555, the clutch member having end clutch faces alternatively engageable with the clutch jaws 59c, 59d as the clutch member is axially shifted in opposite direction, and having an intermediate position disengaging the member from either clutch engagement. The clutch sleeves 55a, 5% respectively have fixed thereon the gear 52, and the two gears 55, 56 of the trains previously described, and therefore are respectively connected with the carriage nut sleeve 4| through a gear train including the gears 52, 53 and through a train including the gears 56, 51, 53, these trains operating to drive the nut sleeve 4| in opposite directions according to the engagement of the one or the other of the clutch sleeves by the clutch member 59c. Clutch member 5942 may be shifted by a fork 60, Figs. 4, '7, engaging a suitable annular groove in the clutch member, whereby to drive the carriage in either direction at a feed rate, or to centrally position the clutch member, whereby to drive the carriage at a quick traverse rate or to stop the carriage, as will later be more fully described.

For quick traverse rate drive of the cross movement of tool slide 28 in either direction there is provided a reverser clutch generally denoted by the numeral 6|, Fig. 4, which, similarly to reverser clutch 49, includes a plurality of spaced outer clutch members am, 551) respectively associated with groups of clutch friction plates Bic, 6|d, the plates of each group being slidably alternately keyed with the associated outer clutch member and with the sleeve 43, the plates of the different groups being alternatively engageable to drive the different outer clutch members by the means of an axially sli'dable clutch spool Me, which may be shifted in either axial direction to set up the drive through the one or the other clutch member 6| (1, 6H), or to position the spool centrally to interrupt the drive, by the means of suitable shifter means, later more fully described, including a fork member 62, Figs. 4, '7, engaging an annular groove in the spool.

The cross slide quick traverse reverser clutch members 6Ia, Gib are respectively connected to a bevel gear 63 through the gears 84, 65 and to a bevel gear 66 through the gears 67, 68, it being understood that the gears 84, 85, and also the gears 61, 69, are meshed in the actual shaft positions shown in Fig. 3. The bevel gears 03 and 68- each mesh with a bevelgear 69, Fig. 5, which transmits motion to a cross feed screw I0 through a. shaft II, bevel gears I2, 13 and a sleeve I4 slidably splined on the screw, the screw being fixed for axial movement with the cross slide 28, by thrust. bearing means such as I5, and engaging a nut I6 fixed in the carriage.

For feed rate drive of the cross. movement of tool slide 28 there is provided a feed reverser clutch generally denoted by the numeral 'I'I, Fig. 4. Similarly to reverser clutch 59, clutch sleeves 'I'Ia, 111) are rotatably supported on the sleeve 44 and respectively provided on their inner adjacent ends with clutch jaw 110, I701. A clutch member He is slidably keyed 0n sleeve 44 and positioned between the sleeves 'I'Ia, 'I'Ib, the clutch member having end clutch faces alternatively engageable with the jaws 'I'Ic or 'I'Id as the clutch member is shifted in opposite directions, and having an intermediate position disengaging the member I'Ic from either clutch engagement. The,

clutch sleeves 19a, 19?) are respectively fixed with the bevel gears 63, 64 and transmit feed rate and includes an arm 19a carrying a hand grip I portion 19b, and an arm 19c carrying a pin 'I9e, Figs. 2, 8. Lever I9 is normally yieldably retained in central position by detent means including a notched cam 8|, Fig. '7, fixed on shaft 88,

and a spring pressed plunger 82, but when the lever is shifted against the resistance of a spring 83 the pin I9e strikes angularly against the end faces of the one or the other of abutment pins 84a, 8417, Figs. 2, 8. Pins 89a, 841) are carried on oppositely extended arms of a lever 84 fixed on a shaft 86 upon which is also fixed a lever 81 which pivotally carries the quick traverse clutch fork member 50, Figs. 4, 8. The fork member 50 is normally yieldably retained in central clutch disengaging position by opposed spring plungers 88, 89, Fig. 7. When the manual lever I9 is shifted in either direction by the hand grip 79b the carriage quick traverse clutch 49 will be engaged to move the carriage 26 in corresponding direction, by the mechanism described, but immediately when lever I9 is released the quick traverse reverser clutch 49 will also be released from either previously engaged position.

For manual operation of the Carriage, feed reverser clutch 59, Fig. 4, there is provided control mechanism as follows: A lever, generally denoted as 90, Figs. 2, 8, includes an arm portion 990. pivoted on a rotatable sleeve 9| and another portion 90b pivoted on arm 90a by the means of a pivot pin 900, the portion 90b carrying a hand grip 90a. The portion 90b is normally yieldably retained in central position relative to arm 90a by the means of opposed springs 92, 93, Fig. 2. The arm 90a is restrained for rotational movement with the sleeve III by the means of adjustable abutment screws 90 Figs. 8, 8A, respectively engaging opposite sides of a pin 9Ia which is fixed in an arm 9Ib carried on sleeve 9I. The sleeve 9| also has fixed therewith a lever 9.4 which pivotally carries the feed reverser clutch formember 50, Figs. 4, 8. The feed clutch is normally yieldably retained in central disengaged position by opposed spring plungers 95, Figs. 2, 8, respectively bear-ing against opposite sides of the pin 9Ia.. Associated with the hub of lever arm 90a there is a detent mechanism including a spring plunger 90g, Fig. 8, there being notches or sockets. such as 90h, suitably positioned to mark the lever positions.

Interlock means are provided between the described controls for carriage quick traverse reverser clutch 49 and feed reverser clutch 59, as follows: The plunger 82, Figs. '7, 8, 9, which cooperates with cam 8I as previously described, at its upper end has an angular face 82a engaging a complementary angular face 960. on a plunger 96, the last mentioned plunger being normally urged to the right in Fig. 8 by a spring 91 operating on a lever 98 which is fixed on a shaft 99. Shaft 99 also has fixed therewith a lever arm I00, Figs. 8, 9, normally retained in the position shown in Fig. 8 by the spring 91, but forced upwardly therefrom by the cam 81, plunger 60 and rod 96 whenever the lever I9 is shifted to engage quick traverse clutch 49 in either direction. The feed lever portion 90b carries spaced abutment pins I-0I, I02, Figs. 8, 9, and whenever the feed lever 90 is shifted to engage the feed clutch one orthe other of these pins moves past the end of lever I00 and springs into engagement behind the lever end in a position of abutment normally preventing disengagement of the feed clutch as long as the lever I90 remains in the position shown in Fig. 8 or until the feed clutch lever is manually reversely shifted to swing the engaged pin downwardly. But if lever I00v is shifted upwardly from the position of Fig. 8, as will occur, for example, when quick traverse clutch lever I9 is shifted to either clutch engaged position, such upward movement will free the engaged pin IM or I02 and the mechanism previosly described will then immediately shift the feed clutch to disengaged position. For manual disengagement of the feed clutch the feed lever portion 90b which carries the abutment pins IOI, I02 may be manually swung about the pivot pin 900 to disengage the engaged abutment pin, as previously pointed out.

For power operated disengagement of the feed clutch 59, there is provided a multiple-stop device generally denoted by the numeral I93, Figs. 1, 2, 14. Stop device I03 includes a sleeve I 04, Fig. 14, rotatably mounted on carriage 28 and carrying a number of adjustably projecting stop screws such as I05, which may be locked in adjusted position by lock screws such as I06, the stop screws I05 being at equal distance from the axis of the sleeve I84 to be rotatable one at a time into position to contact, during carriage travel to the left in Fig. 1, an abutment member II", which is suitably adjustably fixed relative to bed 20. The sleeve and stops are normally forced to the left in Fig. 14 by a spring I08 but the continued movement of the carriage after such contact will force the sleeve to the right.

The sliding rod 96 has an angular end portion engaging a complementary angular face IMa of an annular groove in sleeve I04, in any position of sleeve rotation, and during the right-hand sleeve movement, from the position shown in Fig. 14, the rod 96 will be forced outwardly. As previously pointed out, the outer end of rod 36 engages the lever arm 38 fixed on the trip shaft 39 in a manner such that the outward rod movement swings the trip shaft in direction to move the trip arm I30, Figs. 8, 9, upwardly, to effect disengagement of the feed clutch, as previously described.

Means are provided for power disengagement of the quick traverse clutch 49, as follows: The shaft 83, Fig. 2, of quick traverse lever I9, has fixed therewith a lever arm III which carries a pin IIia projecting to engage the forked end of a lever II2 pivoted on a stud II3, the other end of lever II 2 carrying a pin II 2a which projects rearwardly into the path of travel of a dog member H4 which is adjustably fixed, by the means of a screw II ia, on a rod that extends longitudinally of the bed 20. In the present instance the rod 39, primarily used for feed rate control, as previously pointed out, is also used for adjustably mounting the dogs. The arrangement of the transmission and control mechanism is such that the movement of hand lever I9 which effects carriage movement to the left in Fig. 2, also posi tions the trip pin II2a to the left, to be contacted by a dog, such as dog H3, positioned at the left of the carriage, and vice versa. Dogs such as IE4 may be permanently fixed in position to trip the quick traverse movement of the carriage before the carriage reaches the limit of its movement, whereby to prevent damage.

The described transmission and control connections for carriage 23 are such that, provided the feed drive shaft 32, Fig. 4, and quick traverse drive shaft 46 are operated in normal directions, the shifting either of the quick traverse reverser control lever 13 or of the feed reverser control lever 93 to the left in Fig. 1, will effect movement of carriage 26 to the left, and vice versa. The friction type quick traverse reverser clutch 49 is adapted to slip under overload, whereby to prevent damage if the positive jaw type feed reverser clutch 59 should, by accident, be manually engaged at the same time that the quick traverse clutch is being manually retained in engagement. For the normal control operations the feed and quick traverse levers 92, I9 may be independently operated to effect the desired rate and direction of carriage travel, but the described interlock means insures that an engaged feed clutch will be immediately automatically tripped out of either direction of engagement when the quick traverse clutch is engaged in either direction and, in addition to preventing damage, such interlock means permits the operator to effect either direction of quick traverse instantly, by operation of only a single control lever, irrespective of whether the feed clutch was or was not previously engaged. The separate feed and quick traverse levers, each independently controlling the resulting direction of carriage travel are of material benefit in avoiding confusion of the operator such as may arise, for example, where a single lever effects various results according to movements in different paths.

For manual operation of the cross slide quick traverse reverser clutch BI, Fig. 4, there is provided control mechanism as follows: A lever generally denoted as II5, Figs. 1, 3, is pivoted on a stud H6 and includes an arm IIBa carrying a hand grip portion H52). Fixed with the arm portion II5a there is a pin III. Lever I I5 is normally held in central position, as later described, but when the lever is swung in the one or the other direction about its pivot the projecting end I I'Ia, Fig. 11, of pin II'I strikes angularly against the end faces of the one or the other of abutment pins H3, II 9 which are respectively carried on oppositely projecting ends of a lever I20, Figs. 11, 12, which is fixed with a shaft I2I. Also fixed on shaft I2I there isa lever I22, which is extended for the slotted end I220. thereof to engage a pin I23 fixed with a vertically movable rod I24, Figs. 7, 11. At its lower end the row I24 carries another pin I25 engaging the slotted end of arm I28a of a bell crank I26 which is carried for pivoted movement on the projecting end of a shaft I2'I, Figs. 7, 12, and has another arm I26?) projecting downwardly and pivotally carrying the quick traverse clutch fork member 62, Figs. 4, '7. The fork member 62 is normally held in central clutch disengaging position by opposed spring plungers I28, I29, Fig. '7. When the manual lever H5 is shifted in either direction by the hand grip II5b the cross slide quick traverse clutch 3| will be engaged to move the cross slide 28 in corresponding direction, but immediately when lever H5 is released the quick traverse reverser clutch will also be released from either previously engaged position.

For manual operation of the cross slide feed reverser clutch 11, Fig. 4, there is provided control mechanism as follows: A lever generally denoted as I33, Figs. 2, 3, 11, includes an arm portion I33a having a pivot pin I3I, Figs. 11, 12, and another portion I331) pivoted on arm I3Ila by the means of a pivot pin I330, the portion I332) carrying a hand grip I306. The portion I331) is normally retained in central position relative to arm I331: by the means of opposed springs I32, I33, Fig. 11, in a manner similar to that shown for the similar arm portion 932), Fig. 2, which therefore need not here be described in detail. The lever portion I331; provides a bell crank portion I33 Figs. 11, 12, 13, engaging a suitable recess in an arm I340; of a member I35 which is carried on the shaft I27 and is restrained for rotational movement with the shaft by the means of adjustable abutment screws I35, I35, Figs. 11, 13, respectively engaging opposite sides of a pin I 31 which is rigidly fixed in an arm portion I2ia that is integrally formed as an enlarged head portion of the shaft I21. The shaft I21 also has fixed therewith, on its inner end, an arm I38, Figs. '7, 12, which pivotally carries the feed reverser clutch fork member I8, Figs. 4, 7. The feed clutch is normally yieldably retained in central disengaged position by opposed spring plungers I39, I 39, Figs. 2, 11, respectively bearing against opposite sides of the pin I3I. Associated with the hub of member I 34, Fig. 11, there is a detent mechanism including a spring plunger I40, there being notches or sockets, such as MI, suitably positioned to mark the position of lever II5.

Interlock means are provided between the controls for cross slide quick traverse reverser clutch 6i and feed reverser clutch H, as follows: A multiple arm lever generally denoted by the numeral 542, Figs. 2, 3, is carried on a pivot pin I43, and has an arm portion I42a carrying a pin I44 cooperating with a cam portion M5 fixed on the lever I I5, and another arm portion I422) carrying an abutment member I420. The lever I42 is normally urged in the direction for pin I44 to engage cam I45 by any suitable means, such as a spring I42d operating on another arm I42e of the lever. In the central position of the lever II5, wherein the quick traverse clutch 6| is disengaged, the pin I44 is engaged in a notch I'45a in the cam portion I45, and abutment portion I420 then is in the position shown in- Fig. 3, but will be forced upwardly by the operation of cam I45 on the pin I44 whenever the quick traverse lever I I is shifted to engage quick traverse clutch 6| in either direction. The feed lever-portion I301) carries two spaced abutment pins I46, I41, Fig. 3, and whenever the feed lever I30 is shifted to engage the feed clutch 11, one or the other of pins I46, I41 moves past the abutment member M20 'and springs into engagement behind the abutment member to normally prevent the disengagement of the feed clutch as long as the abutment member remains in the normalposition shown in Fig. 8, or until the feed clutch lever is reversely manually shiftedto swing the engaged abutment pin downwardly about the pivot I 300-, Fig. 11, of the lever portion I301). But if the abutment I420 is shifted upwardly from the position shown in Fig. 3, as will occur, for example, by operation of the cam I45 on pin- I4'4 when quick traverse lever H5 is shifted to either clutch engaged position, such upward movement will free the engaged abutment pin I46 or I41 and the mechanism previously described will then immediately shift the feed clutch 11 to disengaged position. For manual disengagement of the feed clutch the feed lever portion I30a' which carries the abutment pins I46, I41 may be swung about the pivot pin I300 to free the engaged abutment pin, as previously pointed out.

The cross slide feed reverser clutch 11 may be power operated by trip mechanism as follows: A plunger I48, Figs. 2, 3, 6, is carried on carriage 26. v The lower plunger end rests against an adjustable' abutment screw I49 which is carried by the lever arm I42e, and in the normal position of the abutment member I420, that is to say, in the position shown in Fig. 3, the upper end of plunger I48 projects upwardly into the path of movement' of dogs I50, I5I which are adjustabl'y fixed at the side of cross slide 28, see Fig. 3,-by the means of a Tslot I52 and T bolts such as I53. When either dog I50, I5I is positioned to contact the plunger I48, during travel of the cross slide in either direction the plunger will be forced downwardly in Fig. 3, whereby to swing lever I42 to move the abutment member I42c upwardly, out of engagement with either abutment pin I46, I41, and thereby to disengage the feed clutch as previously explained.

The cross slide quick traverse reverser clutch 6| may be power operated by trip mechanism as follows: A trip post or pivot shaft I54, Figs. 3, 6, has fixed on the upper end thereof a trip member I54a carrying an upstanding trip pin portion I54b, which projects into the path of movement of trip pins I55, I56, Figs. 2, 3, which are rigidly fixed in spaced positions on cross slide 28. At its lower end the post I54 has fixed thereon a member I51, Figs. 3, 6, which has a lever end I51a projecting within a suitable slot or socket I58 in the lever portion I I5a of the quick traverse lever II 5. The construction is such that when the quick traverse lever H5 is shifted in a direction to effect rearward movement of the cross slide 28 the lever end I51 will be contacted to swing the trip pin I54 forwardly, and vice versa, where'- by in either direction of quick traverse movement the trip pin will be positioned to be contacted and shifted back to central position by the one or the other of trip pins I55, I56, effecting disengagement of the quick traverseclutch before the cross slide has reached the limit of its movement.

The described transmission and control connections for cross slide 2-8 are such that, provided the feed drive shaft 3-2, Fig. 4, and quick traverse drive shaft 40 are rotated in the normal direction required to effect the direction control effects previously pointed out for carriage 26, similar direction control efiects will be had for the cross slide. That is to say, the shifting either of the quick traverse reverser control lever I I5 or of the feed reverser control lever I30 to the left in Fig.

3 will effect movement of the cross slide 28 to the left, and vice versa. Similarly, the advantages of use of friction type .quick traverse clutches and of independently operable but interlocked feed and quick traverse levers, previously described for the carriage transmission and control mechanism, apply also to the described transmission and control mechanism of the cross slide.

Means are provided for manual movement of both the carriage 26 and of the cross slide 28. For the cross slide movement a hand wheel I56, Figs. 1, 5, is fixed directly on the cross feed screw 10, together with associated-deal mechanism, in the usual manner. For the carriage movement, a hand'wheel I60, Figs. 1, 10, is carried on an arm I60a and is connected with the sleeve nut ,4 I, Figs.

4,10, by the means of a sleeve I'6I, meshed gears I62, I63, shaft I64, meshed gears I65, I66, a shaft I61, and a bevel gear I68 which meshes with a bevel gear I69 fixed on the nut sleeve.

What is claimed is:

1. In a lathe, the combination of a bed, a horizontal work spindle rotatably supported adjacent one end of said bed, a tool carriage guided on said bed for reciprocatory movement parallel with theaxis of said spindle, and transmission and control mechanism for said carriage movement including rotatable feed" rate and quick traverse rate members each axially parallel with said spindle, a plurality of shiftable reversers respectively for connecting different of said ro-' tatablefmembers for movement of said carriage and each shiftable to intermediate motion interrupti'ng position, said re've'rsers being collectively operable for carriage actuation in either direction of said reciprocatory"movement at either of said rates, a plurality of manually operable shifters respectively for different of "said reversers, and means for shifting one of said reversers to inter rupting position upon shifting of the other reverser to either direction position thereof.

2. In a lathe, the combination of a bed, a horizontal work spindle rotatably supported adj'acent one endof said bed, a tool carriage guided on said bed for reciprocat'ory movement parallel with the axis -of said spindle, and transmission and control mechanism for said carriage movement including rotatable feed rate and quick traverse rate members each axially parallel with said spindle, a plurality of shiftable reversers respectively for connecting different of saidrotatable members for movement of said carriage and each shiftable to intermediate motion interrupting position, said reversers being collectively operable for carriage actuation in either direction ofsaidireciprocatory movement ateither of said rates, and a plurality of shifter means respectively for diflerent of said reversers and each including a hand grip porti'on'ca'rried in said carriage for bodily movement therewith and for movement relative to the carriage in a path substantially parallel to the path of carriage movement, the hand grip portion for each of said shifter means being connected for reverser operation to effect carriage movement in the same direction that the hand grip is moved.

3. In a lathe, the combination of a bed, a horizontal work spindle rotatably supported adjacent one end of said bed, a tool carriage guided on said bed for reciprocatory movement parallel with the axis of said spindle, and transmission and control mechanism for said carriage movement including rotatable feed rate and quick traverse rate members each axially parallel With said spindle, a plurality of shiftable reversers respectively for connecting diiferent of said rotatable members for movement of said carriage and each shiftable to intermediate motion interrupting position, said reversers being collectively operable for carriage actuation in either direction of said reciprocatory movement at either of said rates, a plurality of shifter means respectively for diiferent of said reversers and each including a hand grip portion carried in said carriage for bodily movement therewith and for movement relative to the carriage in a path substantially parallel to the path of carriage movement, the hand grip portion for each of said shifter means being connected for reverser operation to effect carriage movement in the same direction that the hand grip is moved, and means for shifting one of said reversers to interrupting position upon shifting of the other reverser to either direction position thereof.

4. In a lathe the combination of a bed, a horizontal work spindle rotatably supported adjacent one end of said bed, a tool carriage guided on said bed for reciprocatory movement in a path parallel with the axis of said spindle, a quick traverse rate train including reverser shiftable friction clutch means for alternatively connecting or disconnecting the train and said carriage, a feed rate train including reverser positive clutch means for alternatively connecting or disconnecting the train and said carriage, and control means for said trains including a plurality of hand grips each carried by said carriage for bodily movement therewith, said hand grips being respectively connected for shifting different of said reverser clutch means.

5. In a lathe the combination of a' bed, a hori zontal work spindle rotatably supported adjacent one end of said bed, a tool carriage guided on said bed for reciprocatory movement in a path parallel with the axis of said spindle, a quick traverse rate train including reverser shiftable to effect carriage movement in the same direction that the hand grip is moved.

6. In a lathe the combination of a bed, a hori-" zontal' work spindlerotatably supported adj acent:

one end of said bed, a tool carriage guided on said bed for reciprocatory movement in. a path' parallel with the axis of said spindle, a quick traverse rate train including reverser shiftable friction clutch means for alternatively connecting or disconnecting the train and said carriage, a feed rate train including reverser positive clutch means for alternatively connecting or disconnecting the train and said carriage, control means for said trains including a plurality of hand grips each carried by said carriage for bodilymovement therewith, said hand grips being respectively connected for shifting diiferent of said reverser clutch means, and means for effecting disconnection of said feed rate train reverser upon engagement of said quick traverse rate train reverser in either direction position thereof.

7; In a lathe the combination of a bed, a horizontal tool spindle rotatably supported adjacent one end of said bed, a tool carriage guided on said bed for reciprocatory movement parallel with the axis of said spindle, a transmission for said reciprocatory movement including alternatively engageable or disengageable reverser clutch means, control means for engaging said reverser clutch means and retaining the clutch means in engaged position, and trip means operative to effect a disengaged position of said reverser clutch means during the carriage movement resulting from said engaged reverser clutch position. I

8. In a lathe the combination of a bed, a horizontal tool spindle rotatably supported adjacent one end of said bed, a tool carriage guided on said bed for reciprocatory movement parallel with the axis of said spindle, a transmission for said reciprocatory movement including alternatively engageable or disengageable reverser clutch means, control means for engaging said reverser clutch means and retaining the clutch means in engaged position, and trip means operative to eifect a disengaged position of said reverser clutch means during the carriage movement resulting from said engaged reverser clutch position, and trip means including a trip member, a plurality of trip elements selectively 'movable one at a time into a position to contact said member during the last mentioned carriage movement, and a trip connection operative to shift said reverser clutch means in accordance with said trip member and element contact.

9. In a lathe the combination of a bed, a horizontal work spindle rotatably supported adjacent one end of said bed, a tool carriage member guided on said bed for reciprocatory movement in a path parallel with the axis of said spindle, a cross slide member guided on said carriage for reciprocatory movement in a path transverse to said spindle axis, transmission mechanismfor movement of said carriage member and of said cross slide member including elements shiftable to effect either member movement alternatively at feed or quick traverse rate in either direction of the reciprocatory movement thereof, and control means for said transmission mechanism including a plurality of pairs of shiftable hand grips each carried on said carriage member, the different pairs respectively controlling shifting of said transmission elements to eiiect the carriage member and cross slide member movement and the diiferent hand grips of each pair controlling the shifting of said elements respectively to effect feed rate and quick traverse rate movement.

"10. In a lathe the combination of a bed, a horizontal work spindle rotatably supported adjacen't one end of said bed, a tool carriage member guided on. said bed .for reciprocatory moveverse to said spindle axis, transmission mech anism for movement of said carriage member and of said cross slide member including elements'collectively shiftable to effect either member movement alternatively at feed or quick travv erse rate in either direction'of. the reciprocatory movement thereof, and control means for said transmission mechanism including a plurality of pairs of shiftable hand grips each carried on said carriage member, the different pairs respectively controlling shifting of said transmission elements to effect the carriage member and cross slide member movement and the different hand grips of each pair controlling the shifting of said elements respectively to effect feed rate and quick traverse rate movement, said control means including a plurality of interlock means respectively associated with different said pairs of hand grips and each operative to disconnect a feed rate connection of said elements effected by the pair when the hand grips of the pair are shifted to effect a quick traverse rate connection of said elements.

11. In a lathe the combination of a bed, a horizontal work spindle rotatably supported adjacent one end of said bed, a tool carriage member guided on said bed for reciprocatory movement in a path parallel with the axis of said spindle, a cross slide member guided on said carriage for reciprocatory movement in a path transverse to said spindle axis, transmission mechanism for movement of said carriage member and of said cross slide member including elements collectively shiftable to eifect either member movement alternatively at feed or quick traverse rate in either direction of the reciprocatory movement thereof, a first pair of hand grips carried on said carriage member for bodily movement therewith and each movable in a path substantially parallel with the carriage member movement, a second pair of hand grips carried on said carriage member for bodily movement therewith and each movable in a path substantially parallel with the cross slide member movement, transmission control connections operable between said shiftable transmission elements and the different hand grips of said first pair respectively to eifect feed rate and quick traverse rate movement of said carriage member, and transmission control connections operable between said shiftable transmission elements and the different hand grips of said second pair respectively to effect feed rate and quick traverse rate movement of said cross slide member.

12. In a lathe the combination of a bed, a horizontal work spindle rotatably supported adjacent one end of said bed, a tool carriage member guided on said bed for reciprocatory movement in a path parallel with the axis of said spindle, a cross slide member guided on said carriage for reciprocatory movement in a path transverse to said spindle axis, transmission mechanism for movement of said carriage member and of said cross slide member including elements collectively shiftable to effect either member movement alternatively at feed or quick traverse rate in either direction of the reciprocatory movement thereof, a first pair of hand grips carried on said carriage member for bodily movement therewith and each movable in a path substantially parallel with the carriage member movement a second pair of hand grips carried on said carriage member for bodily movement therewithllandxeach movable ina path substan-' tially parallel: with the cross slide member movement, transmission. control connections operable betweensaid shiftable transmission elements'and theldifierentjhand grips of said first pair respectively to effect, feed rate and quick traverse rate movementv of said carriage member, transmission control connections operable between said shiftable transmissiorrelements and the difierent hand gripsofsaidesecond pair respectively to effect feed rate and quick traverse rate movement of said cross slide member, and interlock means associated with said transmission control connections and operative to disconnect a feed rate connection of each of said members when the hand grips controlling the member are shifted to effect a quick traverse rate connection thereof.

13. In a lathe the combination of a bed, a horizontal work spindle rotatably supported adjacent one end of said bed, a tool carriage member guidedon said bed for reciprocatory movement in a path parallel with the axis of said spindle, a cross slide member guided on said carriage for reciprocatory movement in a path transverse to said spindle axis, transmission mechanism for movement of said carriage member and of said cross slide member including elements collectively shiftable to effect either member movement alternatively at feed or quick traverse rate in either direction of the reciprocatory movement thereof, a first pair of hand grips carried on said carriage member for bodily movement therewith and each movable in a path substantially parallel with the carriage member movement, a second pair of hand grips carried on said carriage member for bodily movement therewith and each movable in a path substantially parallel with the cross slide member movement, transmission control connections operable between said shiftable transmission'elements and the different hand grips of said first pair respectively to effect feed rate and quick traverse rate movement of said carriage member, and transmission control connections operable between said shiftable transmission elements and the different hand grips of said second pair respectively to effect feed rate and quick traverse rate movement of said cross slide member, said transmission connection being effective upon shifting of a hand grip of either of said pairs to effect movement of the member controlled thereby in the direction of the shifting of the hand grip.

14. In a lathe the combination of a bed, a horizontal work spindle rotatably supported adjacent one end of said bed, a tool carriage guided on said bed for reciprocatory movement in a path parallel with the axis of said spindle, feed rate and quick traverse rate shafts each carried by said bed and spaced apart in mutual parallelism with said spindle axis, a shiftable feed rate reverser and a shiftable quick traverse rate reverser each carried by said carriage for bodily reciprocatory movement therewith and respectively driven from said feed rate shaft and from said quick traverse rate shaft, and a plurality of manually operable controllers each carried by said carriage for reciprocatory movement therewith and respectively connected for operation of the different reversers whereby to actuate a tool carried on said carriage from one or the other of said shafts.

15. In a lathe the combination of a bed, a horizontal work spindle rotatably supported adjacent one end of said bed, a tool carriage member guided on said bed for reciprocatory movement in a path parallel with the spindle axis, a cross slide member guided on said carriage member for reciprocatory movement in a path transverse to the spindle axis, feed rate and quick traverse rate shafts each carried by said bed and spaced apart in mutual parallelism with said spindle axis, a plurality of shiftable feed rate reversers each driven from said feed rate shaft, a plurality. of 10 quick travers rate reversers each driven from said quick traverse rate shaft, each of said reversers being carried by said carriage member for bodily reciprocatory. movement therewith, and control means carried by said carriage member includingmeans shiftable for alternative connection of one of said feed rate reversers or of one of said quicktraverse rate reversers for movement of said carriage member and means shiftable for alternative connection of the other of said feed rate reversers or the other of said quick traverse rate reversers for movement of said cross slide member.

WERNER IRVING SENGER. 

